Overflow downdraw glass forming method and apparatus

ABSTRACT

The present invention significantly modifies “The Overflow Process”. It includes a method and apparatus for measuring glass flow rate and maintaining a constant glass flow rate. It also embodies design features and methods that support and stress the forming apparatus in a manner such that the deformation that results from thermal creep is corrected, thus minimizing the effect of the thermal creep on the thickness variation of the glass sheet. The present invention also embodies design features that change the process from a single step (combined flow distribution and cooling) to a two step process; step one being flow distribution and step two being cooling.

REFERENCE TO RELATED APPLICATIONS

This application claims an invention, which was disclosed in thefollowing Provisional Applications:

-   -   1) Provisional Application No. 60/589,535, filed Jul. 20, 2004,        entitled “GLASS FLOW RATE CONTROL FOR SHEET GLASS FORMING        APPARATUS”;    -   2) Provisional Application No. 60/655,077, filed Feb. 22, 2005,        entitled “SHEET GLASS FORMING APPARATUS”;    -   3) Provisional Application No. 60/659,533, filed Mar. 8, 2005,        entitled “METHOD AND APPARATUS FOR OVERFLOW DOWNDRAW PROCESS        GLASS SHEET THICKNESS CONTROL”; and    -   4) Provisional Application No. 60/662,661, filed Mar. 17, 2005,        entitled “METHOD AND APPARATUS FOR OVERFLOW DOWNDRAW PROCESS”.

The benefit under 35 USC §119(e) of the United States provisionalapplications is hereby claimed, and the aforementioned applications arehereby incorporated herein by reference.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The invention pertains generally to the manufacture of glass sheets,and, more particularly, to glass sheets formed from an overflow process.

2. Description of Related Art

The glass that is used for semiconductor powered display applications,particularly for TFT/LCD display devices that are widely used forcomputer displays, must have very high surface quality to allow thesuccessful application of semiconductor type material. Sheet glass madeusing the apparatus of U.S. Pat. No. 3,338,696, assigned to Corning,Inc., makes the highest quality glass as formed and does not requirepost-processing. That patent makes glass by a manufacturing processtermed “The Overflow Process”. Glass made using other processes requiresgrinding and/or polishing and thus does not have as fine a surfacefinish. The glass sheet must also conform to stringent thicknessvariation and warp specifications. The fine surface finish is formedfrom virgin glass primarily from the center of the glass stream. Thisglass has not been in contact with foreign surfaces since the stirringoperation.

The teachings of U.S. Pat. No. 3,338,696 are still the state of the artas practiced today; however, the apparatus has limitations.

A drawback of the apparatus of “The Overflow Process” is that, eventhough it makes excellent glass during stable operating conditions, thecontrol of process temperature and flow is limited by simplistic controltechnology, thus allowing unintended process transients which causeglass defects. Defects caused by the flow and temperature transientseventually subside when the process stabilizes; however, there is aperiod of time where the quality of the glass sheet is substandard. Flowand temperature transients also cause variations in the sheet thickness.Therefore, there is a need in the art for measurement technology thatfacilitates more precise control of the flow rate of the glass enteringthe forming apparatus.

Another drawback of the apparatus of “The Overflow Process” is that theforming apparatus deforms during a manufacturing campaign in a mannersuch that the glass sheet no longer meets the thickness specification.This is a primary cause for premature termination of the production run.Therefore, there is a need in the art for technology that corrects forthe apparatus deformation.

Another drawback of the apparatus of “The Overflow Process” is that theproduction rate of the present forming apparatus design is limited bythe use of a single step process to both distribute the glass and coolthe glass prior to drawing the sheet. The limited production rate makesthe cost of the glass sheet that is produced less competitive in themarket.

SUMMARY OF THE INVENTION

The present invention significantly modifies “The Overflow Process”. Itincludes a method and apparatus for measuring glass flow rate andmaintaining a constant glass flow rate. It also embodies design featuresand methods that support and stress the forming apparatus in a mannersuch that the deformation that results from thermal creep is corrected,thus minimizing the effect of the thermal creep on the thicknessvariation of the glass sheet. The present invention also embodies designfeatures that change the process from a single step (combined flowdistribution and cooling) to a two step process; step one being flowdistribution and step two being cooling.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 shows the principle parts of “The Overflow Process” sheet glassmanufacturing system.

FIG. 2 shows a prior art heated downcomer pipe with two zones oftemperature control.

FIG. 3 shows a heated downcomer pipe with two zones of temperaturecontrol in an embodiment of the present invention.

FIG. 4 shows a heated downcomer pipe with controlled heat loss to theenvironment in an embodiment of the present invention.

FIG. 5 shows a heated cooling pipe and a heated downcomer pipe withmultiple zones of temperature control in an embodiment of the presentinvention.

FIG. 6 shows a heated cooling pipe with controlled heat loss to theenvironment and a heated downcomer pipe with multiple zones oftemperature control in an embodiment of the present invention.

FIG. 7 shows a heated cooling pipe with controlled heat loss to theenvironment and a heated downcomer pipe with multiple zones oftemperature control and controlled heat loss to the environment in anembodiment of the present invention.

FIG. 8A is a side view of the prior art overflow downdraw sheet glassforming apparatus.

FIG. 8B is a cross-section of the forming block shown in FIG. 8A acrosslines B-B.

FIG. 8C is a top view of the prior art overflow downdraw sheet glassforming apparatus.

FIG. 8D is a cross-section of the forming block shown in FIG. 8A acrosslines D-D.

FIG. 9A is an illustration of the thermal creep deformation of the glassforming block under the load of its own weight.

FIG. 9B is an illustration of the thermal creep deformation of the glassforming block under an applied load that minimizes vertical deformation.

FIG. 9C is an illustration of the thermal creep deformation of the glassforming block under excessive applied load.

FIG. 9D is an illustration of the thermal creep deformation of the glassforming block under an applied load that minimizes vertical deformationover the extended period of a production campaign.

FIG. 10 shows the magnified shape of the forming block with the sagcorrection by prior art applied force as determined by a finite elementanalysis (FEA).

FIG. 11A is a side view of an embodiment of the present invention thatshows compression loading of the trough bottom, which is applied bycompression inserts inserted into cavities at each end of the formingblock.

FIG. 11B is a cross-section of the forming block shown in FIG. 11Aacross lines B-B.

FIG. 11C is a top view of the embodiment shown in FIG. 11A.

FIG. 11D is a cross-section of the forming block shown in FIG. 11Aacross lines D-D.

FIG. 11E is a cross-section of the embodiment shown in FIG. 11C acrosslines E-E that shows multi-stage compression loading of the troughbottom.

FIG. 12 shows the magnified shape of the embodiment of this inventionshown in FIGS. 11A through 11E with the sag corrected as determined byFEA.

FIG. 13A is a side view of an embodiment of the present invention thatshows multi-stage compression loading of the trough bottom, which isapplied by compression blocks inserted into cavities at each end of theforming block.

FIG. 13B is a cross-section of the forming block shown in FIG. 13Aacross lines B-B.

FIG. 13C is a top view of the embodiment shown in FIG. 13A.

FIG. 13D is a cross-section of the forming block shown in FIG. 13Aacross lines D-D.

FIG. 13E is a cross-section of the embodiment shown in FIG. 13C acrosslines E-E that shows multi-stage compression loading of the troughbottom.

FIG. 14A is a side view of another embodiment of the present inventionthat shows two stage compression loading of the trough bottom.

FIG. 14B is a cross-section of the forming block shown in FIG. 14Aacross lines B-B.

FIG. 14C is a top view of the embodiment shown in FIG. 14A.

FIG. 14D is a cross-section of the forming block shown in FIG. 14Aacross lines D-D.

FIG. 14E is a cross-section of the embodiment shown in FIG. 14C acrosslines E-E that shows multi-stage compression loading of the troughbottom.

FIG. 15 shows the magnified shape of the forming block with the sagcorrection by a multi-stage applied force as determined by FEA.

FIG. 16 shows the magnified shape of the forming block with the sagresultant from a 20 percent lower multi-stage applied force asdetermined by FEA.

FIG. 17 shows the magnified shape of the forming block with variedinflow end multi-stage applied forces as determined by FEA.

FIG. 18 shows the magnified shape of the forming block with varied farend multi-stage applied forces as determined by FEA.

FIG. 19 shows the magnified shape of the prior art forming block withthe sag resultant from a 20 percent lower prior art applied force asdetermined by FEA.

FIG. 20 shows the magnified shape of the forming block trough lateralthermal creep deflection caused by hydrostatic pressure as determined byFEA.

FIG. 21A is a side view of the prior art glass forming block.

FIG. 21B is an end view of the prior art glass forming block.

FIG. 22A is a side view of the thermal environment of the prior artglass forming block.

FIG. 22B is an end view of the thermal environment of the prior artglass forming block.

FIG. 23A is a side view of the two step forming process in an embodimentof the present invention.

FIG. 23B is an end view of the two step forming process in an embodimentof the present invention.

FIG. 24A is a side view of the two step forming process showing coolingblock compression loading and glass flow in an embodiment of the presentinvention.

FIG. 24B is an end view of the two step forming process shown in FIG.24A.

FIG. 25A is a side view of a cooling block in the two step formingprocess showing two methods of edge director heating in an embodiment ofthe present invention.

FIG. 25B is an end view of the cooling block in FIG. 25A showing onemethod of edge director heating in an embodiment of the presentinvention.

FIG. 25C is a top view of the edge director in FIG. 25A showing onemethod of edge director heating in an embodiment of the presentinvention.

DETAILED DESCRIPTION OF THE INVENTION

The present invention provides technology for measurement of glass flowrate as it enters the forming apparatus of the sheet manufacturingprocess and discloses a procedure for regulating this process flow. Aspresently practiced in the prior art, the measurement of glass flow rateis determined by the quantity of the product produced at the end of theproduction line. The present invention incorporates energy balanceinformation and preferably uses representative measurements of the glassstream temperature as outlined in U.S. Pat. No. 6,895,782 and patentapplication Ser. No. 11/011,657, as contrasted with prior artmeasurements of the temperature of the outer surface of the processpiping.

The glass “Sheet Forming Apparatus” normally designed for use in “TheOverflow Process” (U.S. Pat. No. 3,338,696) relies on a specificallyshaped forming block to distribute the glass in a manner to form sheetof a uniform thickness. The basic shape of this forming block isdescribed in detail in U.S. Pat. No. 3,338,696. The sheet glass formingprocess is conducted at elevated temperatures, typically between 1000°C. and 1350° C. At these temperatures the materials used forconstruction of the forming block exhibit a property called thermalcreep, which is deformation of the material caused by applied stress atelevated temperatures. Thus, the forming block sags and deforms underthe stress caused by its own weight and the stress caused by thehydrostatic pressure of the glass in the forming block trough. In theprior art a counteracting force is introduced at each end of the formingblock to prevent the forming block sag. This force, however, cannotfully correct for the distributed force introduced by the weight of theforming block, thus the thickness distribution of the glass sheetmanufactured is not fully corrected.

This invention introduces a method for using either the prior art forcedevice or a multi-stage force device to further minimize the distortionof the forming block trough and weirs when the forming block changesshape under the influence of thermal creep.

In the prior art “Overflow Process” the glass flows into the top portionof the one piece forming block at a viscosity of approximately 25,000poise, flows over the forming block weirs and down the sides of theforming block, where it is cooled to the drawing viscosity ofapproximately 100,000 poise. This represents a cooling of the glass ofapproximately 75° C. The range of cooling is limited by the verticaldimension of the forming block. The cooling range could be increased to100-200° C. if the forming block were vertically larger, however,current refractory manufacturing technology limits the size of theforming block.

The present invention isolates the forming block in a separate chamberat a much higher temperature. This allows the glass to be at asignificantly lower viscosity, thus allowing a greater glass flow in thesame size forming block. The glass is then fed to a cooling block in aseparate chamber. This chamber has a large vertical dimension such thatthe glass can be cooled to the temperature required by the formingviscosity of approximately 100,000 poise.

The molten glass flow from the melting furnace and forehearth, which ispreferably of substantially uniform temperature, chemical compositionand flow rate, enters the forming apparatus through the inlet pipe tothe sheet forming trough. The glass sheet forming apparatus is describedin detail in U.S. Pat. No. 3,338,696 entitled “SHEET FORMING APPARATUS”,issued Aug. 29, 1967, U.S. Pat. No. 6,748,765 entitled “OVERFLOWDOWNDRAW GLASS FORMING METHOD AND APPARATUS”, issued Jun. 15, 2004, U.S.Pat. No. 6,889,526 entitled “OVERFLOW DOWNDRAW GLASS FORMING METHOD ANDAPPARATUS”, issued May 10, 2005, U.S. Pat. No. 6,895,782 entitled“OVERFLOW DOWNDRAW GLASS FORMING METHOD AND APPARATUS”, issued May 24,2005, patent application Ser. No. 10/826,097 entitled “SHEET GLASSFORMING APPARATUS”, filed Apr. 16, 2004, patent application Ser. No.11/006,251 entitled “SHEET GLASS FORMING APPARATUS”, filed Dec. 7, 2004,patent application Ser. No. 11/011,657 entitled “SHEET GLASS FORMINGAPPARATUS, filed Dec. 14, 2004, and patent application Ser. No.11/060,139 entitled “SHEET WIDTH CONTROL FOR OVERFLOW DOWNDRAW SHEETFORMING APPARATUS”, filed Feb. 17, 2005. All of these U.S. patents andpatent applications are herein incorporated by reference.

Referring to FIG. 1, a typical “Overflow Process” manufacturing system(1) is shown. The glass (12) from the melting furnace (2) and finer (3),which must be of substantially uniform temperature and chemicalcomposition, feeds a stirrer (4). The stirrer (4) thoroughly homogenizesthe glass. The glass (12) is then conducted through a cooling pipe (5),into a bowl (6), and down into the downcomer pipe (7), through the joint(14) between the downcomer pipe (7) and the forming apparatus inflowpipe (8), to the inlet of the overflow forming block (11). While flowingfrom the stirrer (4) to the forming block (11), the glass (12),especially that which forms the sheet surface, must remain homogeneous.The bowl (6) alters the flow direction from horizontal to vertical andin some applications provides a means for stopping the flow of glass(12). A needle (16) is provided to stop glass flow. The normal functionof the downcomer pipe (7) is twofold. It conducts the glass from thebowl (6) to the trough inflow pipe (8) and controls the flow rate of theglass stream entering the process. The downcomer pipe (7) is carefullydesigned such that by maintaining it at a specific temperature thedesired glass stream flow rate is precisely maintained at the desiredvalue. The joint (14) between the downcomer pipe (7) and the troughinflow pipe (8) allows for removal of the sheet glass forming apparatusfor service and compensations for the thermal expansion of the processequipment.

The Reynolds number is the ratio of inertial forces to viscous forcesand is used to determine whether a flow is laminar or turbulent. Laminarflow occurs at low Reynolds numbers and turbulent flow occurs at highReynolds numbers. Glass is a Newtonian fluid and its flow is laminar.Typical Reynolds Numbers are many orders of magnitude below a ReynoldsNumber of 1000, which is the rule of thumb for transition from laminarflow to turbulent flow. Laminar flow is characterized by the flow ratebeing controlled by the viscosity of the flowing medium and allparticles following uniform predictable paths; whereby there is nomixing in the flow stream. The viscosity of glass, however, is a verystrong function of temperature. Therefore, it is important to accuratelycontrol the temperature of the glass to control the flow rate of theglass.

The downcomer pipe (7) is the primary glass flow control device for theforming block (11). The downcomer pipe (7) is dynamically matched to theforming block (11) design to produce glass of the required thicknessprofile. Prior art operation recommends operating both at the sameconstant temperature. This is recommended because the downcomer pipe (7)and the forming block (11) are oil modeled with constant temperature oilas a unit to certify the design prior to construction.

FIG. 2 shows the prior art downcomer pipe (7) system. The glass (12)flows through the platinum pipe (22), which is heated by one or moreelectric heating elements (21) and (24). Heat loss to the environment islimited by the insulation jacket (25). A cooling jacket (27), throughwhich cooling gases (28) flow, often encases the system. The power ofthe heating elements (21) and (24), the thickness of the insulationjacket (25), and the quantity of cooling gases (28) determine the rangeof operation for the glass flow (12) through the downcomer pipe (7)system. The flow rate of the glass (12) is primarily controlled by thepower in the heating elements.

The thermocouples (20), (23), (26), and (29) are representative ofcommon practice in the prior art as they are shown touching the outsidesurface of the platinum pipe (22) containing the flowing glass.Measurement of the temperature of the outside surface of the platinumpipe is the preferred practice in the prior art, and thermocouples havebeen mounted accordingly. It is common to control the temperature of theflowing glass to a predetermined level by maintaining the readings ofthe thermocouples constant. Typically the power to the heating element(21) would be regulated to maintain the temperature at location (23)constant as measured by thermocouple (23), and the power to the heatingelement (24) would be regulated to maintain the temperature at location(26) constant as measured by thermocouple (26). Another procedurepracticed in the prior art uses the reading of thermocouple (29) tocontrol the power in the heating element (21).

Measurement and Control of Glass Flow Rate

In an embodiment of the present invention, the temperature of the moltenglass stream is accurately measured at two or more different pointsalong the downcomer pipe. Further, heat flow is carefully controlled byheating elements and optional cooling jackets at multiple locationsalong the downcomer pipe. Finally, a controlled and constant glass flowrate is maintained by use of the equations derived in this applicationfrom energy balance equations on the system.

The operating parameters that determine the glass flow rate are theviscosity of the glass stream and the available static pressure. If theprocess has a free surface in the bowl, the level of glass in the bowldetermines the static pressure available for flow. If the bowl has asealed top, the static pressure available to flow the glass isdetermined by the operating conditions in the other parts of the systemextending back to and including the stirrer (4). The viscosity of theglass is a function of the glass chemistry and the glass temperature.The chemistry varies considerably; however, this occurs over a fairlylong time period and does not affect the minute to minute flowvariations. The glass viscosity is inferred by the measurement of glasstemperature. Note that the measurement of the temperature of the outsideof the platinum pipe (22) is not representative of the average viscosityof the glass stream and is therefore a potential source of error. It ispreferable to use thermocouples inserted into the glass stream whichgive a representative measurement of the glass stream temperature asoutlined in U.S. Pat. No. 6,895,782 and patent application Ser. No.11/011,657.

The following derivation produces the equations used in embodiments ofthe present invention to maintain a constant glass flow rate during theglass forming process, thereby producing sheet glass of a constantthickness. The derivation also produces the equations used to set theflow rate of the glass during the glass forming process in embodimentsof the present invention, thereby producing sheet glass of a desiredthickness. The derivation is based on four assumptions, which arediscussed in further detail following the derivation.

Referring to FIG. 3 the equations for the heat flow Q in the downcomerpipe (7) are:Q ₃₀ =w _(g) ×c×T ₃₀  Eq. (1)Q ₃₁=Electric Power at (31)  Eq. (2)Q ₃₂ =h ₃₂ ×A×(T ₃₂ −T _(amb))+ε₃₂ ×σ×A×(T ₃₂ ⁴ −T _(amb) ⁴)  Eq. (3)Q ₃₃ =w _(g) ×c×T ₃₃  Eq. (4)Q ₃₄=Electric Power at (34)  Eq. (5)Q ₃₅ =h ₃₅ ×A×(T ₃₅ −T _(amb))+ε₃₅ ×σ×A×(T ₃₅ ⁴ −T _(amb) ⁴)  Eq. (6)Q ₃₆ =w _(g) ×c×T ₃₆  Eq. (7)where:

-   -   w_(g) =glass (12) flow rate    -   c=glass specific heat, assumed constant, therefore d(c)=0    -   T=temperature    -   h=convection heat transfer coefficient, assumed constant,        therefore d(h)=0    -   ε=emissivity, assumed constant, therefore d(ε)=0    -   σ=Stefan-Boltzmann constant    -   A=surface area for heat transfer

Heat (31) and (34) is added to the glass by the heating elements (21)and (24), and heat (32) and (35) is lost to the ambient (amb)environment along the downcomer pipe.

Writing the energy balance equations:Q ₃₃ =Q ₃₀ +Q ₃₁ −Q ₃₂  Eq. (8)Q ₃₆ =Q ₃₃ +Q ₃₄ −Q ₃₅  Eq. (9)Substituting Eq. (8) into Eq. (9) and transposing produces:Q ₃₆ −Q ₃₀=(Q ₃₁ +Q ₃₄)−(Q ₃₂ +Q ₃₅)  Eq. (10)Substituting Eq. (1) and Eq. (7) into Eq. (10):w _(g) ×c×(T ₃₆ −T ₃₀)=Q ₃₁ +Q ₃₄−(Q ₃₂ +Q ₃₅)  Eq. (11)Taking the derivative of Eq. (11):w _(g) ×c×d(T ₃₆ −T ₃₀)+d(w _(g))×c×(T ₃₆ −T ₃₀)=d(Q ₃₁)+d(Q ₃₄)−d(Q ₃₂+Q ₃₅)  Eq. (12)

As Assumption 1, let d(Q₃₁)+d(Q₃₄)=0 This assumes a constant totalelectrical energy input. Therefore:w _(g) ×c×d(T ₃₆ −T ₃₀)+d(w)×c×(T ₃₆ −T ₃₀)=−d(Q ₃₂ +Q ₃₅)  Eq. (13)

As Assumption 2, let d(Q₃₂+Q₃₅)=0. This assumes a constant heat loss tothe ambient environment. Therefore:w _(g) ×d(T ₃₆ −T ₃₀)+d(w _(g))×(T ₃₆ −T ₃₀)=0  Eq. (14)

If both w and (T₃₆−T₃₀) are finite then if the process is controlledsuch that (T₃₆−T₃₀) is constant and therefore d(T₃₆−T₃₀)=0:

-   -   d(w_(g))=0 and the flow of glass is controlled such that the        flow rate is constant.

If d(T₃₆−T₃₀) is not zero, then d(w _(g)) is not zero, and an error inthe glass flow is produced, which is corrected in an embodiment of thepresent invention.

The flow of glass is changed and the condition d(T₃₆−T₃₀)=0 ismaintained by changing the energy distribution. Referring to FIG. 3 theequation for the glass mass flow rate w is:w _(g) =K ₁ ×η×Δp  Eq. (15)where:

-   -   K₁=flow coefficient of pipe    -   η=glass viscosity    -   Δp=pressure difference

The glass viscosity is a function of temperature and is linearized forthe temperature range considered by the present invention with thefollowing equation:w _(g) =K ₀ ×T ^(k) ×Δp+K ₂  Eq. (16)where:

-   -   K₀ and K₂=constants of proportionality    -   k=temperature exponent on the order of −10 to −20 for the        glasses of interest

Therefore the partial derivatives of the glass flow rate at the threemeasurement points (30), (33), and (36) in the downcomer pipe withrespect to temperature are:∂w _(g) /∂T ₃₀ =−k×w _(g) /T ₃₀  Eq. (17)∂w _(g) /∂T ₃₃ =−k×w _(g) /T ₃₃  Eq. (18)∂w _(g) /∂T ₃₆ =−k×w _(g) /T ₃₆  Eq. (19)The partial differential equation of the mass flow equation is:

Δw_(g) =∂w _(g) /∂T ₃₆ ×ΔT ₃₆ +∂w _(g) /∂T ₃₃ ×ΔT ₃₃ +∂w _(g) /∂ ₃₀ ×ΔT₃₀ +∂w _(g) /∂p ₃₆ ×Δp ₃₆ +∂w _(g) /∂p ₃₀ ×Δp ₃₀  Eq. (20)

As Assumption 3, let Δp₃₆ and Δp₃₀ equal 0, which makes each of the lasttwo terms of Eq. (20) equal to zero:Δw _(g) =∂w _(g) /∂T ₃₆ ×ΔT ₃₆ +∂w _(g) /T ₃₃ ×ΔT ₃₃ +∂w _(g) /∂T ₃₀ ×ΔT₃₀  Eq. (21)

As Assumption 4, for a stable process let T₃₆ and T₃₀ be constant, butallow T₃₃ to be variable. Therefore:Δw _(g) =∂w _(g) /∂T ₃₃ ×ΔT ₃₃  Eq. (22)Δw _(g) =−k×w _(g) /T ₃₃ ×ΔT ₃₃  Eq. (23)

An apparatus of the present invention controls the mass flow rate(w_(g)) by changing the intermediate temperature T₃₃ while maintainingthe total energy constant as constant, i.e. d(Q₃₁)+d(Q₃₄)=0. This changein flow rate caused by changing the intermediate temperature provides acorrection to the flow rate error as indicated by d(T₃₆−T₃₀).

FIG. 4 shows another embodiment of the present invention, whereadditional heat control is provided by the incorporation of at least twocooling jackets (41) and (44) for controlled heat removal. In thisembodiment, the heating elements (21) and (24) are used in combinationwith the cooling jackets (41) and (44) to add heat to the system andremove heat from the system, respectively, in a controlled manner.Referring to FIG. 4 the equations for the heat flow Q in the downcomerpipe (7) are:Q ₃₀ =w _(g) ×c×T ₃₀  Eq. (24)Q ₂₁=Electric Power from (21)  Eq. (25)Q ₄₃ =w _(a42) ×c _(p)×(T ₄₃ −T ₄₂)  Eq. (26)Q ₃₃ =w _(g) ×c×T ₃₃  Eq. (27)Q ₂₄=Electric Power from (24)  Eq. (28)Q ₄₆ =w _(a45) ×c _(p)×(T ₄₆ −T ₄₅)  Eq. (29)Q ₃₆ =w _(g) ×c×T ₃₆  Eq. (30)where:

-   -   w_(g) =glass (12) flow rate    -   w_(a)=cooling air flow    -   c=glass specific heat, assumed constant, therefore d(c)=0    -   c_(p)=specific heat of air at constant pressure    -   T=temperature    -   h=convection heat transfer coefficient, assumed constant,        therefore d(h)=0

Heat is added to the glass by the heating elements (21) and (24) andheat is lost to the ambient environment via the cooling jackets (41) and(44). The inlet air flow (42) and (45) to the cooling jackets has alower temperature than the outlet air flow (43) and (46) leaving thecooling jackets.

Writing the energy balance equations:Q ₃₃ =Q ₃₀ +Q ₂₁ −Q ₄₃  Eq. (31)Q ₃₆ =Q ₃₃ +Q ₂₄ −Q ₄₆  Eq. (32)Substituting Eq. (31) into Eq. (32) and transposing produces:Q ₃₆ −Q ₃₀=(Q ₂₁ +Q ₂₄)−(Q ₄₃ +Q ₄₆)  Eq. (33)Substituting Eq. (24) and Eq. (30) into Eq. (33):w _(g) ×c×(T ₃₆ −T ₃₀)=Q ₂₁ +Q ₂₄−(Q ₄₃ +Q ₄₆)  Eq. (34)Taking the derivative of Eq. (34):w _(g) ×c×d(T ₃₆ −T ₃₀)+d(w _(g))×c×(T ₃₆ −T ₃₀)=d(Q ₂₁)+d(Q ₂₄)−d(Q ₄₃+Q ₄₆)  Eq. (35)

As Assumption 1, let d(Q₂₁)+d(Q₂₄)=0 This assumes a constant totalelectrical energy input. Therefore:w _(g) ×c×d(T ₃₆ −T ₃₀)+d(w)×c×(T ₃₆ −T ₃₀)=−d(Q ₄₃ +Q ₄₆)  Eq. (36)

As Assumption 2, let d(Q₄₃ +Q ₄₆)=0. This assumes a constant heat lossto the ambient environment via the cooling jackets. Therefore:w _(g) ×d(T ₃₆ −T ₃₀)+d(w _(g))×(T ₃₆ −T ₃₀)=0  Eq. (37)

Eq. (37) is identical to Eq. (14) and the rest of the derivation is thesame as for the embodiment shown in FIG. 3. The embodiment of FIG. 4allows heat to be added and heat to be removed in a controlled manner toinsure constant heat loss to the ambient environment.

FIG. 5 shows another embodiment of the present invention, which includesthe downcomer pipe (7) of FIG. 3, a cooling pipe (5) and a bowl (6). Inthis embodiment, the glass flow rate is measured in the cooling pipe (5)and glass flow rate control is implemented in the downcomer pipe (7).The cooling pipe (5) is designed with at least two thermocouples (50)and (56) and at least one heating element (51). The downcomer pipe (7)is designed with at least two thermocouples (30) and (36) and optionallya third thermocouple (33), preferably at least two heating elements (21)and (24), and an insulation jacket (25). Following is the derivation forimplementing glass flow rate measurement in the cooling pipe (5).

Referring to FIG. 5 the equations for the heat flow Q in the coolingpipe (5) are:Q ₅₀ =w _(g) ×c×T ₅₀  Eq. (38)Q ₅₁=Electric Power at (51)  Eq. (39)Q ₅₂ =h ₅₂ ×A×(T ₅₂ −T _(amb))+ε₅₂ ×σ×A×(T ₅₂ ⁴ −T _(amb) ⁴)  Eq. (40)Q ₅₆ =w _(g) ×c×T ₅₆  Eq. (41)

Heat is added to the glass by a heating element (51) and heat (52) islost to the ambient (amb) environment along the cooling pipe (5).

Writing the energy balance equation:Q ₅₆=Q₅₀ +Q ₅₁ −Q ₅₂  Eq. (42)Transposing:Q ₅₆ −Q ₅₀ =Q ₅₁ −Q ₅₂  Eq. (43)Substituting Eq. (38) and Eq. (41) into Eq. (43)w _(g) ×c×(T ₅₆ −T ₅₀)=Q ₅₁ −Q ₅₂  Eq. (44)Taking the derivative of Eq. (44):w _(g) ×c×d(T ₃₆ −T ₃₀)+d(w _(g))×c×(T ₃₆ −T ₃₀)=d(Q ₅₁)−d(Q ₅₂)  Eq.(45)

As Assumption 1, let d(Q₅₁)=0 This assumes a constant total electricalenergy input. Therefore:w _(g) ×c×d(T ₃₆ −T ₃₀)+d(w _(g))×c×(T ₃₆ −T ₃₀)=−d(Q ₅₂)  Eq. (46)

As Assumption 2, let d(Q₅₂)=0. This assumes a constant heat loss to theambient environment. Therefore:w _(g) ×c×d(T ₅₆ −T ₅₀)+d(w _(g))×c×(T ₅₆ −T ₅₀)=0  Eq. (47)Dividing by c:w _(g) ×d(T ₅₆ −T ₅₀)+d(w _(g))×(T ₅₆ −T ₅₀)=0  Eq. (48)

If both w_(g) and (T₅₆−T₅₀) are finite and if the process is controlledsuch that (T₅₆−T₅₀) is constant (d(T₅₆−T₅₀)=0):

-   -   d(w_(g))=0 and the flow of glass is controlled such that the        flow rate is constant.

If d(T₅₆−T₅₀) is not zero, then d(w _(g)) is not zero, and an error inthe glass flow is produced, which is corrected in an embodiment of thepresent invention.

In this embodiment of the invention the cooling pipe (5) is used as themeasure of glass flow rate. The energy input from the heating element(51) and the energy lost to the ambient environment are constant.Therefore any change in the temperature difference between the glassentering (50) and the glass exiting (56) is indicative of a change inglass flow (12).

Equations 15 through 23 are applied in the same manner as the previousembodiments to change the impedance of the downcomer and control theglass (12) flow rate to the sheet glass forming apparatus (11).

FIG. 6 shows another embodiment of the present invention, whereadditional heat control is provided by the addition of a cooling jacket(67) to the cooling pipe (5) for controlled heat removal. In thisembodiment the heating element (51) is used in combination with thecooling jacket (67) to add heat to the system and remove heat from thesystem, respectively, in a controlled manner. This substantiallyimproves the accuracy of the measurement of the glass (12) flow rate.Referring to FIG. 6 the equations for the heat flow Q in the coolingpipe (5) are:Q ₅₀ =w _(g) ×c×T ₅₀  Eq. (49)Q ₅₁=Electric Power at (51)  Eq. (50)Q ₆₉ =w _(a68) ×c _(p)×(T ₆₉ −T ₆₈)  Eq. (51)Q ₅₆ =w _(g) ×c×T ₅₆  Eq. (52)

Heat is added to the glass by a heating element (51), and heat (69) islost to the ambient (amb) environment via the cooling jacket (67). Theinlet air flow (68) to the cooling jacket has a lower temperature thanthe outlet air flow (69) leaving the cooling jacket.

Writing the energy balance equation:Q ₅₆ =Q ₅₀ +Q ₅₁ −Q ₆₉  Eq. (53)Transposing:Q ₅₆ −Q ₅₀ =Q ₅₁ −Q ₆₉  Eq. (54)Substituting Eq. (49) and Eq. (52) into Eq. (54)w _(g) ×c×(T ₅₆ −T ₅₀)=Q ₅₁ −Q ₆₉  Eq. (55)Taking the derivative of Eq. (55):w _(g) ×c×d(T ₃₆ −T ₃₀)+d(w _(g))×c×(T ₃₆ −T ₃₀)=d(Q ₅₁)−d(Q ₆₉)  Eq.(56)

As Assumption 1, let d(Q₅₁)=0 This assumes a constant total electricalenergy input. Therefore:w _(g) ×c×d(T ₃₆ −T ₃₀)+d(w _(g))×c×(T ₃₆ −T ₃₀)=d(Q ₆₉)  Eq. (57)

As Assumption 2, let d(Q₆₉)=0. This assumes a constant heat loss to theambient environment via the cooling jacket. Therefore:w _(g) ×c×d(T ₅₆ −T ₅₀)+d(w _(g))×c×(T ₅₆ −T ₅₀)=0  Eq. (58)Dividing by c:w _(g) ×d(T ₅₆ −T ₅₀)+d(w _(g))×(T ₅₆ −T ₅₀)=0  Eq. (59)

If both w_(g) and (T₅₆−T₅₀) are finite and if the process is controlledsuch that (T₅₆−T₅₀) is constant (d(T₅₆−T₅₀)=0):

-   -   d(w_(g))=0 and the flow of glass is controlled such that the        flow rate is constant.

If d(T₅₆−T₅₀) is not zero, then d(w _(g)) is not zero, and an error inthe glass flow is produced, which is corrected in an embodiment of thepresent invention.

In this embodiment of the invention the cooling pipe (5) is used as themeasure of glass flow rate. The energy input from the heating element(51) and the energy removed by the cooling jacket (67) are eachmaintained constant. Therefore any change in the temperature differencebetween the glass entering (50) and the glass exiting (56) is indicativeof a change in glass flow (12).

Equations 15 through 23 are applied in the same manner as the previousembodiments to change the impedance of the downcomer pipe and controlthe glass (12) flow rate to the sheet glass forming apparatus (11).

FIG. 7 shows another embodiment of the present invention, where afurther addition of heat control is provided by the addition of coolingjackets (41) and (44) to the downcomer pipe (7) for controlled heatremoval. The cooling jacket (67) on the cooling pipe (5) is the mostimportant as it improves the accuracy of the glass (12) flow ratemeasurement. Although not as important, the cooling jackets (41) and(44) added to the downcomer pipe (7) provide additional stability to thecontrol of glass (12) flow by the downcomer pipe (7).

Discussion of the Assumptions

Four assumptions were made as part of this derivation. Justification andaction to implement are discussed below:

Assumption 1—Constant Total Electrical Energy Input

This assumption is easily implemented, as there is complete control overthe electric power equipment.

Assumption 2—Constant Heat Loss to the Ambient

For short term operation on many systems, constant convection andradiant heat loss is a valid assumption. If long term stability of theheat loss to the ambient is required, a controlled cooling jacket may beincluded in the design. FIG. 4 shows two such cooling jackets (41) and(44) for the downcomer pipe (7), each for individual control zones (21)and (24). The air flow (42) and (45) into each cooling jacket (41) and(44) is controlled to a value such that the heat extracted is constant.The air flow (43) and (46) out of the cooling jackets has a highertemperature than the air flow in (42) and (45). FIG. 6 shows a coolingjacket (67) for the cooling pipe (5). The inlet air flow (68) to thecooling jacket (67) is controlled such that the heat extracted isconstant. The outlet air flow (69) has a higher temperature than theinlet air flow (68).

The energy equations for air are the same as for glass but withdifferent values for the coefficients:Q ₄₃ =w _(a42) ×c _(p)×(T ₄₃ −T ₄₂)  Eq. (60)Q ₄₆ =w _(a45) ×c _(p)×(T ₄₆ −T ₄₅)  Eq. (61)Q ₆₉ =w _(a68) ×c _(p)×(T ₆₉ −T ₆₈)  Eq. (62)The general form of the above equations is:Q _(x) =w _(a,y) ×c _(p)×(T _(x) −T _(y))  Eq. (63)Taking the derivative:d(Q _(x))=w _(a,y) ×c _(p) ×d(T _(x) −T _(y))+d(w _(a,y))×c _(p)×(T _(x)−T _(y))  Eq. (64)let d(Q_(x))=0 (Constant heat loss)therefore:d(w _(a,y))=−w _(a,y)/(T _(x) −T _(y))×d(T _(x) −T _(y))  Eq. (65)The value of Q_(x) in each case is maintained constant by varying theair flow d(w_(a,y)) thus maintaining the value ofw_(a,y)×c_(p)×(T_(x)−T_(y)) constant for each cooling jacket using Eq.(65).Assumption 3—Constant Pressure

The downcomer pipe (7) exit pressure p₃₆ is substantially constant, asit is a function of the free surface in the forming apparatus inflowpipe (8). There is a low impedance to flow in the inflow pipe (8) suchthat the level of the glass free surface in the inflow pipe (8) is closeto the same level of the glass overflowing the weirs at the inflow endof the forming block (11). Therefore (Δp₃₆=0) is a valid assumption. Thedowncomer pipe (7) inlet pressure is dependent on the upstream processand therefore Δp₃₀=0 is not a good assumption for normal operation. Ifthe bowl (6) has a free surface, then p₃₀ is a function of the glasslevel in the bowl (6). If the bowl top is sealed, p₃₀ is a function ofthe glass level in the stirrer chamber (4) and the flow parameters ofthe stirrer chamber (4), the flow parameters of the cooling pipe (5),and the flow parameters of the bowl (6). If p₃₀ is not at the normaloperating condition then Eq. (66) is used to compensate for changes inp₃₀:∂w _(g) /∂T ₃₃ ×ΔT ₃₃ +∂w _(g) /∂p ₃₀ ×Δp ₃₀=0  Eq. (66)Assumption 4—Constant Temperature

A process objective is to maintain the downcomer pipe exit temperatureT₃₆ constant, as this is the inlet temperature to the forming apparatusinflow pipe. The downcomer pipe inlet temperature T₃₀ is dependent onthe upstream process and therefore ΔT₃₀=0 is not a good assumption fornormal operation. The stated objective of this flow control method is tocontrol the glass flow constant by maintaining (T₃₆−T₃₀) at a fixedvalue. This cannot be done if T₃₀ varies and T₃₆ must be maintained at afixed value. The error in T₃₀ is compensated by applying Eq. (67):Δ(Q ₃₁ +Q ₃₄)=w _(g) ×c×Δ(T ₃₀)  Eq. (67)where:

-   -   Δ(T₃₀)=difference between the desired and actual T₃₀        Application of this Invention to the General Class of Platinum        Delivery Systems

The method and apparatus of the present invention can also be used tomeasure and regulate glass flow in platinum delivery systems for othermanufacturing processes, which require optical quality glass including,but not limited to lenses for eyeglasses, telescopes, microscopes, LCDglass, and projection televisions. A platinum delivery system for aprocess other than the overflow process normally includes a finer (3), astirrer (4), and a cooling pipe (5), similar to those of the overflowprocess; however, the bowl (6) and the downcomer pipe (7) of theoverflow process are replaced by a device that fulfills the requirementsof the specific manufacturing process, to which the glass is beingsupplied. If this device is not adaptable to the invention herein,either the finer (3) or the cooling pipe (5), or both in combination areused as described below in the application of the present invention.

Application of this Invention to the Finer

The method and apparatus of the present invention is also used in thefiner (3) as a measure of glass flow rate and to implement glass flowrate control. The finer (3) is designed with thermocouples, heatingelements, insulation jackets, and cooling jackets in the same manner asthe downcomer pipe and the same strategy for the measurement and controlof glass flow rate is used. Placement of the thermocouples in the glassstream of the finer (3) is normally not detrimental to glass quality asthe glass is mixed in the stirrer (4), if a stirrer (4) is installed,after passing through the finer (3). The finer vents (17) are locationswhere thermocouples are preferably inserted for glass temperaturemeasurement.

Application of this Invention to the Cooling Pipe

The method and apparatus of the present invention is also used in thecooling pipe (5) as a measure of glass flow rate and to implement glassflow rate control. The cooling pipe (5) is preferably designed withthermocouples, heating elements, insulation jackets, and cooling jacketsin the same manner as the downcomer pipe, and the same strategy for themeasurement and control of glass flow rate is used. The temperaturedifference between the glass entering the cooling pipe (5) and the glassexiting the cooling pipe (5) is normally quite large, i.e. 200° C. Alarge temperature difference increases the accuracy of the glass flowrate measurement.

Application of this Invention to the Combination of a Finer and aCooling Pipe

The method and apparatus of the present invention is also used in thecombination of the finer (3) and the cooling pipe (5) as a measure ofglass flow rate and to implement glass flow rate control. The finer (3)and cooling pipe (5) is preferably designed with thermocouples, heatingelements, insulation jackets, and cooling jackets in the same manner asthe downcomer pipe, and the same strategy for the measurement andcontrol of glass flow rate is used. In a preferred embodiment thecombination of the finer (3) and cooling pipe (5) can be treated thesame as the two heating elements in FIG. 3 and equations 1 through 23applied. Heating element (21) represents the finer (3) and heatingelement (24) represents the cooling pipe (5). In the same manner,another preferred embodiment is represented by the equations associatedwith FIG. 4. In other preferred embodiments, the equations associatedwith FIGS. 5, 6, and 7 are alternatively applied to different heatingand cooling configurations of the combination of the finer (3) and thecooling pipe (5).

Placement of Thermocouples in the Glass Stream

Referring to FIGS. 3, 4, 5, 6, and 7, a preferred embodiment of thepresent invention includes immersing the thermocouples (30), (33), (36),(50), and (56) directly in the process stream to measure accurately thetemperature of the flowing glass at the important locations in thecooling pipe (5) and the downcomer pipe (7). These thermocouples areplaced such that they will not have an adverse effect on the sheet glassquality. The thermocouples are preferably immersed in locations directlyin the path of molten glass flow where defects caused by the flow ofglass in proximity of the thermocouples end up in the unusable beads ateither end of the formed glass sheet. The placement of thesethermocouples is discussed further in U.S. Pat. No. 6,895,782, andpatent application Ser. No. 11/011,657.

Prevention and Correction of Forming Block Deformation

The refractory materials from which the forming block and its supportstructure are made have high strength in compression and low strength intension. Like most structural materials they also change shape whenstressed at high temperature by a process termed “Thermal Creep”. Thesematerial characteristics and how these characteristics effect themanufacturing process provided motivation for the present invention.

FIGS. 8A-8D illustrate the principle parts of a typical “OverflowProcess” forming apparatus in more detail than shown in FIG. 1. Themolten glass (12) from the melting furnace and forehearth, which must beof substantially uniform temperature and chemical composition, entersthe forming apparatus through the downcomer pipe (7) and flows into thesheet forming block (11) trough. The glass sheet forming apparatus,which is described in detail in both U.S. Pat. Nos. 3,338,696,6,889,526, and 6,895,782, and patent application Ser. No. 11/011,657, isa wedge shaped forming block (11). Straight sloped weirs (84)substantially parallel with the pointed edge of the wedge, herein termedthe root (15), form each side of the forming block trough. The formingblock trough bottom (86) and the sides of the trough are contoured in amanner to provide even distribution of glass to the top of each sideweir (84). The molten glass (12) then flows through the forming block(11) trough, over the top of each side weir (84), down each side of thewedge shaped forming block (11), and joins at the root (15) to form asheet of molten glass. The molten glass is then cooled as it is pulledoff the root (15) to form a solid glass sheet (13) of substantiallyuniform thickness.

FIGS. 9A-9D illustrate the typical effects of thermal creep on the shapeof the forming block (11) when the forming block end support blocksimpart different compression stress in the bottom of the forming block(11) near the root (15). FIG. 9A shows that with no compression loadingthe forming block (11) sags in the middle such that the top of the weirs(84) and the root (15) are now curved (91) and the trough bottom (86)has a change in curvature (91). This curvature (91) causes the moltenglass (12) to no longer flow with constant thickness (92) over the weirs(84). This curvature (91) allows more glass to flow over the middle ofthe weirs resulting in an uneven sheet thickness distribution. Theforming block (11) has an initial length (90) as defined by the phantomlines (94) and (99). With no external loading the weirs (84) get shorterand the root (15) gets longer. FIG. 9B shows that sagging of the formingblock is minimized under the optimum compression loading (96) of thelower section of the forming block (11) near the root (15). With optimalloading both the weirs (84) and the root (15) shorten equally to length(97). FIG. 9C shows that if too much load (95) is applied to the lowersection of the forming block (11) near the root (15), the root (15) iscompressed excessively, thus producing a convex shape (93) to theforming block weirs (84), the forming block trough bottom (86), and theroot (15). The root (15) shortens considerably more than the weirs (84)as can be seen by the movement relative to the phantom lines (94) and(99). FIGS. 9A through 9C represent the effect of thermal creep over thesame time period. FIG. 9D shows a forming block (11), which hasshortened a greater amount to length (98), since imparting the correctload allows a substantially longer production campaign. This increasedshortening now has an adverse effect on the width of the sheetmanufactured.

FIG. 10 shows the magnified shape of a typical prior art forming blockas corrected for sagging due to thermal creep. This was a result of afinite element analysis (FEA) to determine the optimal sag correctingforce (96) for a typical forming block. The forming block size chosenfor this example has a weir (84) overflow length of 2 meters, a heightof approximately 0.6 meters and a width of 0.2 meters.

Improved Loading of the Forming Block to Minimize Thermal Creep

FIGS. 11A through 11E show a preferred embodiment of this inventionwhereby inserts (113) and (117) are used to distribute the loadingforces (122) and (128) to both the ends and to the interior of theforming block (111), with weirs (114) and trough bottom (116). Thisinvention is similar to the multi-stage loading device which is aninvention applied for by the inventor of the present application inpatent application Ser. No. 11/060,139; however, in this invention onlyone compression loading device is required at each end of the formingblock. In the present invention, the compression loading of the bottomof the forming block (111) is applied at each end and is distributedinto the interior of the forming block by using inserts (113) and (117)which have greater thermal creep resistance than the parent material ofthe forming block (111). At the inflow end the bottom of the formingblock (111) insert (113) is loaded by the support and compression block(112) with a force (122). The insert (113) is inserted into a cavity ofdepth (115) and applies force (125) at the bottom of this cavity andforce (123) at the bottom of the inflow end of the forming block (111).At the far end the bottom of the forming block (111) insert (117) isloaded by the support and compression block (118) with a force (128).The insert (117) is inserted into a cavity of depth (119) and appliesforce (129) at the bottom of this cavity and force (127) at the bottomof the far end of the forming block (111). In one embodiment, the depthof cavity (115) and the depth of cavity (119) are independent and rangefrom 0 to 40 percent of a length of the root. More preferably, the depthof cavity (115) ranges from 20 to 35 percent, while the depth of cavity(119) ranges from 10 to 25 percent of a length of the root. The forcebalances at each end are:F ₁₂₂ =F ₁₂₃ +F ₁₂₅  Eq. (68)F ₁₂₈ =F ₁₂₇ +F ₁₂₉  Eq. (69)

FIGS. 11A and 11E show the weight of the forming block (111) supportedby the support and compression blocks (112) and (118). Normally theforce at the inflow end (122) would be equal to the force at the far end(128); however, in some embodiments of this invention it is necessary tohave a small force (110) to seal the inflow pipe to the forming block.In this instance, the force at the far end (128) is larger by force(110) than the force at the inflow end (122) such that:F ₁₂₈ =F ₁₂₂ +F ₁₁₀  Eq. (70)

Alternately force (120) at the top of the far end may be used to providethe sealing force (120). Including force (120), the equation to balancethe forces is:F ₁₂₈ +F ₁₂₀ =F ₁₂₂ +F ₁₁₀  Eq. (71)

FIG. 12 shows the magnified shape of an FEA of the application of apreferred embodiment of this invention to the same size forming block asshown in FIG. 10. Comparison of the resultant shape of the twoapparatuses as shown in FIGS. 10 and 12 show substantially improvedshape control using the present invention.

FIG. 19 shows the magnified shape of the forming block from theapplication of a force (196), which is 80 percent of the optimum force(96). It can be seen from comparison of the forming block shape in FIGS.10, 12, and 19, that a lesser application of force has a substantialinfluence on the corrected shape of the forming block.

FIG. 13A through 13E shows forming block (131) in another embodiment ofthe present invention. The inflow end insert (132) has a stepped shapesuch that it can apply interior forces (133) and (134) at depths (135)and (136), respectively. In this instance the force balance at theinflow end is:F ₁₂₂ =F ₁₃₂ +F ₁₃₃ +F ₁₃₄  Eq. (72)

FIG. 13A through 13E also show an embodiment of the present inventionwhereby the far end insert has a necked shape (139) in the center. Thepurpose of the shaping (139) of the insert (137) is to control therelative magnitudes of the applied surface force (127) and interiorforce (129) as described in the following section. In this instance theforce balance at the far end is:F ₁₂₈ =F ₁₂₇ +F ₁₂₉  Eq. (73)Controlling the Ratio of Surface to Interior Forces

In a preferred embodiment, molybdenum is the material used for theinsert. Platinum cladding of the insert is preferable but not alwaysnecessary to protect the molybdenum from oxidation. Molybdenum has athermal creep resistance on the order of 4 times that of high qualityZircon, which is the material normally used for the forming blocks (111)and (113).

As the forming block in the region of an insert deforms due to thermalcreep the insert is more resistant to the effects of thermal creep anddeforms less, thus increasing the force at the bottom of the cavity.This increased force at the bottom of the cavity in turn increases thedeformation of the insert, until eventually a balance in deformation ofthe forming block and the insert produces a balance in forces.

The design of the cavities and the inserts as they effect the shape ofan individual forming block are determined using FEA. The forces are ofa distributed nature, however, a very rough rule of thumb would beapplied as:

Insert Thermal Creep Constant times Insert Area Equals

Forming Block Thermal Creep Constant times Forming Block CompressionArea

Correction for the Effects of Thermal Creep During the ProductionCampaign

If the shape of the forming block in the production environment exactlyfollowed the results of the physics of the FEA, the manufacture sheetthickness would remain within product specification for the duration ofan extended production campaign. The realities of the manufacturingworld such as material homogeneity, temperature distribution, frictionforces, measurement errors, and human intervention, etc., causedeviation from the theoretical physics. It is important to note thatthese realities do not violate the physics, but cause deviations fromthe assumed physics. This means that the cause and effect ofmathematical and physical analysis as determined by FEA andcomputational fluid dynamics (CFD) still apply.

Single Force Embodiment

The present invention teaches a procedure for maintaining the sheetthickness profile within specification for an extended productioncampaign in spite of the influence of the manufacturing world realitiesnoted above. As an example, if the friction opposing the applied force(96) reduced its effect to the level of force (196) the forming blockwould sag in the middle after a given period of time in the productioncampaign. Intuitively this would produce a sheet which is thicker in themiddle than at each end. The teaching of Dockerty in U.S. Pat. No.3,338,696 and CFD both substantially verify that the sheet would bethicker in the middle. In an embodiment of the present invention theforce (96) is increased to both overcome this friction effect andproduce a reversal of the sagging such that the sheet is now of a moreuniform thickness. This embodiment of the present invention is the mostsimplistic and the correction of the sagged shape is limited. Thedetails of the strategy for correcting the sheet thickness are discussedin the following multi-stage embodiment, but also apply directly to thissimpler single force embodiment.

Multi-Stage Force Embodiment

FIGS. 14A through 14E show a multi-stage loading device which is aninvention applied for by this inventor in patent application Ser. No.11/060,139. Compression loading of the bottom of the forming block(141), which has weirs (144) and trough bottom (146), is applied at eachend by a multi-stage loading device. At the inflow end the bottom of theforming block (141) is loaded by the support and compression block (143)with a force (156) and the compression block (142) with a force (157).The compression block (142) is inserted into a cavity of a depth (145)at the inflow end and applies force (157) at the bottom of the cavity.At the far end the bottom of the forming block (141) is loaded by thesupport and compression block (147) with a force (159) and thecompression block (148) with a force (158). The compression block (148)is inserted into a cavity of depth (149) at the far end and appliesforce (158) at the bottom of this cavity. FIGS. 14A and 14E show theweight of the forming block (141) being supported by the support andcompression blocks (143) and (147). Normally the sum of the forces atthe inflow end “(156) plus (157)” is equal to the sum of the forces atthe far end “(158) plus (159)”; however, in some embodiments of thisinvention it may be necessary to have a small force (140) to seal theinflow pipe to the forming block. In this instance, the sum of theforces at the far end “(158) plus (159)” would be larger by force (140)than the sum of the forces at the inflow end “(156) plus (157)” suchthat:F ₁₅₈ +F ₁₅₉ =F ₁₅₆ +F ₁₅₇ +F ₁₄₀  Eq. (74)

Alternately force (150) at the top of the far end may be used to providethe sealing force (150). Forces (140) and (150) are not included in thecalculations in the embodiments described below; however, they may beused as part of other embodiments to add additional options for thereshaping of the forming block (141). Forces (140) and (150) need not beequal in these embodiments. Including force (150) the equation tobalance the forces is:F ₁₅₈ +F ₁₅₉ +F ₁₅₀ =F ₁₅₆ +F ₁₅₇ +F ₁₄₀  Eq. (75)

FIGS. 15, 16, 17, and 18 show various combinations of multi-stage forceapplication and the magnified effect on forming block shape. It can beseen that the sagged shape shown in FIG. 15, which is the result of anFEA, is an improvement over that of the single force sagged shape ofFIG. 10. FIGS. 16, 17, and 18 also illustrate the versatility in theshapes that are generated by different combinations of the multi-stageforce system. Table 1 gives the force information for FIGS. 15, 16, 17,and 18. The force at each location is given as a percent of the totalforce at each end, which is the condition of FIG. 15. TABLE 1 Force 156Force 157 Force 158 Force 159 40% 60% 20% 80% 32% 48% 16% 64%  0% 100% 20% 80% 40% 60% 60% 40%

There are other parameters that can be used to effect the sheetthickness distribution besides the shape of the forming block. The mostimportant parameters besides the shape of the forming block are the tiltof the forming block and the temperature distribution of the glass as itflows in the forming block. The temperature distribution of the glass iseffected primarily by the radiation to the glass from the siliconcarbide enclosure (228) of the forming block (11). For the purpose ofthe following embodiments it is assumed that the temperaturedistribution is maintained constant and that the tilt is only used tomaintain the average thickness along the length of the sheet constant.

Preferably the design of the forming block and the magnitudes of theapplied forces for the campaign start-up configuration of themulti-stage force system and forming block are determined by iteratingthe design using FEA and CFD. The shape of the forming block may befurther verified by an oil model. Comparing the results of CFD and oilmodeling enhances the capability of each technology.

There are two important steps in developing the technology to correctthe shape of the forming block and thus the sheet thickness distributionduring a manufacturing campaign. They are 1) relating forming blockshape to variations in sheet thickness distribution and 2) relatingapplied forces to forming block shape.

Step 1—Relating Forming Block Shape to Variations in Sheet ThicknessDistribution

In a preferred embodiment, CFD is used to generate a matrix of formingblock deformation to sheet thickness deviations from standard. Inanother preferred embodiment, oil modeling of varied shapes of theforming block is alternately used to generate a matrix of forming blockdeformation to sheet thickness deviations from standard. When astationary error in the sheet thickness distribution is evident, eitheror both of these matrixes is used to estimate the deformed shape of theforming block.

Step 2—Relating Forces to Forming Block Shape

In a preferred embodiment, FEA is used to determine the effect of variedapplied forces on the shape of the forming block. The FEA results ofvaried force combinations of Table 1 are shown in FIGS. 15, 16, 17, and18. An alternative embodiment uses a physical model of the formingblock, whereby the forces are applied to an elastic body of low modulusof elasticity and the deflections measured. A quadratic or higher orderequation is fitted to each forming block shape for each force condition.FIGS. 15, 16, 17, and 18 show forming block shape results for variouscombinations of forces; (156), (157), (158), and (159). In a preferredembodiment, forces (140) and (150) are also included in the analysis.

Correcting Sheet Thickness Distribution during a Manufacturing Campaign

When after a given time period of the production campaign, a stationaryerror in the sheet thickness distribution is evident, the first step isto use the relationships developed above to determine the root cause ofthe error. If the physics of the first principles in the initial designdid not work, it is best to know why the physics did not work.Correction of a basic design error or operational procedure is thepreferred long term solution for the next production campaign.

In a preferred embodiment step 1 (the relationship of forming blockshape to variations in sheet thickness distribution) is used to estimatethe deformed shape of the forming block. A regression of the equationsof step 2 (the relationship of applied forces to forming trough shape)versus the deformed shape of the forming block determines the forceerrors that produced the forming block deformation. Twice the negativeof these force errors would normally produce a corrective action over asimilar time period of the production campaign during which thethickness error occurred. It is important to note that the thermal creepdeformations occurred over a period of time and that corrective actioncan only be effective over a similar time period. Also, there arenon-linearities in the thermal creep deformation process and thereforesmall steps and continuous monitoring and analysis of progress isrequired.

In another preferred embodiment the matrix of step 1 (the relationshipof forming block shape to variations in sheet thickness distribution)and the regression equations of step 2 (the relationship of appliedforces to forming trough shape) are combined. A regression of thiscombined set of equations versus the sheet thickness deviationsdetermines the force errors that produced thickness variation in thesheet. Twice the negative of these force errors would normally produce acorrective action over a similar time period of the production campaignduring which the thickness error occurred. It is important to note thatthe thermal creep deformations occurred over a period of time and thatcorrective action can only be effective over a similar time period.Also, there are non-linearities in the thermal creep deformation processand therefore small steps and continuous monitoring and analysis ofprogress is required.

The regression analysis may be performed either mathematically or bymanual substitution. For matrices and equations that are not fullydeveloped, the mathematical solution often gives erratic results. Manualsubstitution is often the way to a practical solution.

In summary either of the two procedures above or variations of theseprocedures, (mathematical, empirical, or a combination of the two) canbe used to correct sheet thickness distribution during a manufacturingcampaign.

FIG. 20 is an FEA illustration of the effect of hydro-static forces,which cause an additional source of sheet thickness distribution error.A lateral deformation is caused by thermal creep of the forming blocktrough side-wall and weir, which is not addressed in the prior art. InFIG. 20 the forming block (201) is deformed longitudinally approximately5 percent from its original shape (141). The weir (204) is deformed fromits original position (144) both longitudinally and laterally. Thisdeformation causes additional flow to the center of the glass sheet anda thinning of the sheet at the inflow end. The procedure just discussedabove is used to compensate for this phenomenon.

Increase in Production Rate with a Two-Step Process

The refractory material from which the forming block is normally made isisostatically pressed Zircon. A single piece of isostatically pressedZircon is limited in size by Zircon manufacturing technology. Thedrawing of the glass sheet from the root of the forming block in thepresent overflow process occurs at approximately 100,000 poise. U.S.Pat. No. 3,338,696 teaches that the entire forming block would beisothermal at the temperature where the glass at a viscosity ofapproximately 100,000 poise. Isothermal operation requires a trough inthe top of the forming block of dimensions substantially larger than canbe accommodated by present Zircon manufacturing technology. In order tomake the trough a reasonable size the glass flowing into the formingblock trough is at a lower viscosity of approximately 25,000 poise(higher temperature) and then cooled to the forming viscosity ofapproximately 100,000 poise. The higher the inflow temperature (lowerviscosity) the smaller the trough. The greater the difference betweenthe inflow temperature and the forming temperature the greater thecooling requirement, which results in a larger required verticaldimension of the forming block to facilitate the increased coolingrequirement. The present single forming block design is thus acompromise.

FIGS. 21A-21B illustrate the principle parts of a typical “OverflowProcess” forming system. The molten glass (12) from the melting furnaceand forehearth, which must be of substantially uniform temperature andchemical composition, enters the forming apparatus through the inflowpipe (8) and flows into the wedge shaped forming block (11). Straightsloped weirs (84) form each side of a trough at the top of the formingblock (11). The trough bottom (86) and the sides of the trough arecontoured in a manner to provide even distribution of glass to the topof each side weir (84). The molten glass (12) then flows through thetrough in the forming block (11), over the top of each side weir (84),down each side of the wedge shaped forming block (11), and joins at theroot (15) to form a sheet of molten glass. The molten glass is thencooled by radiation as it is pulled off the root (15) by pulling rollers(219) to form a solid glass sheet (13) of substantially uniformthickness.

FIGS. 22A-22B show the prior art forming block (11) in a chamber (223)enclosed by a muffle (228). The muffle (228) is preferably made fromsilicon carbide, a high conductivity material that maintains a suitabletemperature distribution for the glass flow to be distributed uniformlyto form the glass sheet. Sliding doors (224) at the bottom of thechamber have a surface (225) that is at a lower temperature than thechamber interior and thus provides radiant cooling for the glass (222)on the lower portion of the forming block (11). Cooling air is suppliedthrough individually controlled cooling tubes (227) as taught by U.S.Pat. No. 3,682,609, herein incorporated by reference. These coolingtubes (227) control the longitudinal temperature distribution of theglass forming the sheet (13). The sliding doors (224) are adjustablelaterally to control the heat loss from chamber (223) to annealingchamber (221). Below the sliding doors (224) is the annealer (229) whichremoves the internal stresses in the glass sheet (13). The pullingrollers (219) are normally fabricated as part of the annealer (229) andare contained within the temperature controlled annealing chamber (221).

FIGS. 23A-23B show a sheet glass forming apparatus which includes aforming block (11) in a temperature controlled chamber (223) feedingglass to a cooling block (231) in another temperature controlled chamber(233) enclosed by muffle (238), which has sidewalls (239) and endwalls(236). In a preferred embodiment of the present invention, the muffle(238) is made from silicon carbide. The temperature of the sidewalls(239) is at or below the temperature of the glass entering the chamber(233). The temperature of the endwalls (236) may be either greater thanor less than the sidewall (239) temperature in order to control thetemperature of the edges of the flowing glass. In a preferred embodimentthe temperature of the endwalls (236) is within 50° C. of thetemperature of the sidewalls (239). Both the endwalls (236) and thesidewalls (239) have top to bottom and side to side temperaturegradients. The temperature in chamber (233) is substantially lower thanthat in chamber (223) and thus provides controlled cooling of the glassas it flows down each side of the cooling block. In a preferredembodiment the temperature in chamber (233) is 75° C. to 150° C. lowerthan the temperature in chamber (223). Sliding doors (234) at the bottomof the chamber (233) have a surface (235) that is at a lower temperaturethan the chamber interior and thus provides additional radiant coolingfor the glass (232) on the lower portion of the cooling block (231). Thesliding doors (234) are adjustable laterally to control the heat lossfrom chamber (233) to annealing chamber (221). The adjustable slidingdoors (224) serve the dual purpose of cooling the glass on the prior artforming block (11) and providing thermal isolation between temperaturecontrolled chamber (223) and temperature controlled chamber (233).

It is important to control convective heat transfer at certain criticalpoints in the two step process. Convective heat transfer (via aircurrents) must be minimized between the glass (222) on the invertedsurface of the forming block (11) and the sliding door surface (225) andthe glass (232) on the inverted surface of the cooling block (231) andthe sliding door surface (235). This is preferably accomplished byequalizing the localized pressure in chambers (223) and (233) at thesliding door (224) and by equalizing the localized pressure in chambers(233) and (221) at the sliding door (234).

The physics of this invention is best described by an example. Table 2below defines the temperature-viscosity relationship for a typical LCDglass. Assume that the prior art inflow glass temperature is 1255° C.and the forming temperature is 1180° C. This corresponds to an inflowviscosity of 25,000 poise and a forming viscosity of 100,000 poise. Theprior art forming block (11) and the cooling from the prior art slidingdoors (224) must cool the glass 75° C. If double the production rate isrequired using the prior art forming block shape the inflow temperaturemust be 1300° C. which corresponds to halving the viscosity to 12,500poise, which would double the flow rate of the glass. The formingtemperature remains substantially the same, therefore with double theflow rate, the temperature change requirement is now 120° C. This is arequired energy loss increase of 320 percent, 200 percent of which iscaused by the increased glass flow and 160 percent of which is caused bythe increased temperature change (200 percent multiplied by 160 percentequaling 320 percent). In the prior art this would require a much longercooling zone which would translate to a forming block (11) with asubstantially larger vertical dimension and larger sliding doors (224).The present invention adds a second cooling block (231), cooling chamber(233), and additional sliding doors (234). The second cooling block(231) includes a second set of individually controlled cooling tubes(237). Because of the limitation on the size of the Zircon formingblock, adding the second cooling block (231), cooling chamber (233), andthe additional sliding doors (234) is a practical solution to the energyremoval problem. TABLE 2 Temperature Viscosity-poise 1150° C. 200,0001180° C. 100,000 1215° C. 50,000 1255° C. 25,000 1300° C. 12,500

An additional advantage of the separate cooling chamber (233) is thatthe temperature distribution in chamber (223) may be designed tooptimize the function of glass flow distribution, instead of having tobe compromised to also perform the cooling function. U.S. Pat. No.3,338,696 teaches that the chamber (223) surrounding the forming blockshould be at a uniform temperature. This is possible and/or can be moreclosely realized if a compromise is not required to cool the glass tothe temperature required for drawing.

The temperature distribution in the cooling chamber (233) may beoptimized for the cooling function. The drawing temperature of the glassthat is used for LCD display devices has a drawing temperature close tothe glass devitrification temperature. The devitrification temperatureis the temperature at which the glass starts to crystallize, formingnon-transparent defects. The separate cooling chamber allows moreprecise control of glass temperature, thus allowing the operatingdrawing temperature to more closely approach the devitrificationtemperature. Lowering the operational drawing temperature also increasesthe stability of the drawing process.

FIGS. 24A-24B show the cooling block (231) in greater detail. On eachend of the cooling block (231) is a fence (241) to which the verticallyflowing glass (12) attaches in order to overcome the effect of surfacetension. On each end of the bottom of cooling block (231) is an edgedirector (242) to counter the effect of surface tension of the glass(12) when it is flowing on the inverted surfaces (243) of the coolingblock (231). The prior art edge director for the forming block (11) istaught in U.S. Pat. No. 3,451,798, herein incorporated by reference, andmay optionally be used in this application. FIG. 24B shows the glass(12) flowing between the forming block (11) and the cooling block (231)a distance (245). If the distance (245) is too great, the glass (12)flow becomes unstable causing entrapment of bubbles, which arerejectable defects. The maximum distance for stable operation is afunction of glass (12) flow rate and viscosity. In a preferredembodiment the maximum distance is 50 mm. In another preferredembodiment the distance (245) is zero, where the forming block (11) isin contact with the cooling block (231) at one or more longitudinallocations. FIG. 24A also shows support blocks (248) at each end of thebottom of the cooling block (231). Force (246) is applied to eachcooling block to provide a compression stress to counteract thermalcreep deformation of the cooling block (231) caused by gravity acting onthe weight of the cooling block (231), the weight of the glass flowingon the cooling block (231) and the drawing forces of the sheet below thecooling block (231).

FIGS. 25A-25C are detailed views of the cooling block without theflowing glass (12). The edge director (242) used on the cooling block(231) is a novel improvement of the edge director taught in U.S. Pat.No. 3,451,798 in that the intersection of the filleted surface (252) andthe fence (241) is skewed outward away from the center of the coolingblock (231) at an angle (254). This skewed angle makes the sheet wider.The filleted surface (252) of the edge director (242) is shown as aplane, but may optionally be concave. It is a combination of the shapeof the fillet surface (252) and the skewed angle (254) that make theglass stay attached to the fence (241). The shape of fillet surface andthe magnitude of the skew angle may be determined by CFD. It also may bedetermined and/or verified by modeling prior to implementation inproduction in an oil model using the Capillary Number as the parameterof similitude between the oil and the glass. The Capillary Number isequal to the Viscosity times the Velocity divided by the SurfaceTension.

Glass (12) flowing adjacent to the fences (241) and on the edge director(242) fillet surfaces (252) moves substantially slower than the glass(12) flowing on the body of the cooling block (231). Also, the ends ofthe cooling block (231) are likely to be colder than the center of thecooling block. The slower movement, the colder environment or acombination of both make the glass (12) more susceptible todevitrification. Localized heating is provided to overcome this problem.FIGS. 25A and 25B show an embodiment of the present invention wherebyradiant heaters (257) focused specifically on the edge directors (242)provide localized heating. FIGS. 25A and 25C show an embodiment usingelectrical resistance heating of the platinum in the edge director (242)and fence (241) to provide localized heating. Electrical conductors(255) and (256) attached to the top and bottom respectively of the edgedirector (242) are connected to a low voltage/high current electricalpower supply. Electric current passing through the platinum heats theedge director (242). The distribution of the heating is controlled bythe geometry and thickness distribution of the platinum in the edgedirector (242). This direct heating technology is used in otherapplications in the glass industry.

In summary the cooling block embodiment of this invention not onlyincreases the production rate, but also contributes to thecontrollability of the process and quality of the product.

If edge directors are used on the forming block (11), they also may havean intersection of a filleted surface and a fence skewed outward awayfrom the center of the forming block (11) at an angle, similar to theedge directors (242) for the cooling block (231) in FIG. 25. The shapeof the fillet surface and the magnitude of the skew angle for the edgedirectors on the forming block may be determined by CFD. It also may bedetermined and/or verified by modeling prior to implementation inproduction in an oil model using the Capillary Number as the parameterof similitude between the oil and the glass.

Accordingly, it is to be understood that the embodiments of theinvention herein described are merely illustrative of the application ofthe principles of the invention. Reference herein to details of theillustrated embodiments is not intended to limit the scope of theclaims, which themselves recite those features regarded as essential tothe invention.

1. An apparatus for supplying a constant flow of glass to a glass forming process, comprising: a) a downcomer pipe for controlling the flow of molten glass; b) at least two heating elements on an outside of the downcomer pipe; and c) a plurality of thermocouples that measure a temperature of a glass stream at an inflow end and an outflow end of each heating element on the downcomer pipe; wherein an error in a flow rate is determined by a calculation of a balance of energy for the two heating elements; such that an energy may be redistributed to the two heating elements, thus changing an average glass viscosity in the downcomer pipe, such that the flow rate of glass is maintained at a substantially constant value.
 2. The apparatus of claim 1, wherein a total energy remains constant.
 3. The apparatus of claim 1, further comprising a plurality of cooling zones at a same location on the downcomer pipe as the heating elements.
 4. The apparatus of claim 3, wherein the cooling zones measure an energy flux.
 5. The apparatus of claim 1, wherein the thermocouples are immersed in the glass stream.
 6. The apparatus of claim 5, wherein defects caused by a flow of glass in proximity of the thermocouples end up in at least one unusable bead at either end of a formed glass sheet.
 7. A method of supplying a constant flow of glass to a glass forming process, using an apparatus comprising a downcomer pipe for controlling the flow of molten glass, at least two heating elements on an outside of the downcomer pipe, and a plurality of thermocouples that measure a temperature of a glass stream at an inflow end and an outflow end of each heating element on the downcomer pipe, comprising the steps of: a) calculating a balance of energy for the two heating elements to determine an error in a flow rate; and b) redistributing an energy to the two heating elements, thus changing an average glass viscosity in the downcomer pipe, such that the flow rate of glass is maintained at a substantially constant value.
 8. The method of claim 7, wherein a total energy remains constant.
 9. The method of claim 7, further comprising the step of maintaining an outlet temperature of the glass flowing from the downcomer pipe at a fixed value.
 10. The method of claim 7, wherein the apparatus further comprises a plurality of cooling zones at a same location on the downcomer pipe as the heating elements.
 11. The method of claim 10, further comprising the step of measuring an energy flux from the cooling zones.
 12. The method of claim 11, further comprising the step of maintaining the outlet temperature of the glass flowing from the downcomer pipe at a fixed value.
 13. The method of claim 7, wherein the thermocouples are immersed in the glass stream.
 14. The method of claim 13, wherein defects caused by a flow of glass in proximity of the thermocouples end up in at least one unusable bead at either end of a formed glass sheet.
 15. An improved apparatus for supplying a constant flow of glass to a glass forming process, wherein the apparatus includes a cooling pipe for cooling the glass, a downcomer pipe for controlling the flow of molten glass, and a bowl for connecting the cooling pipe to the downcomer pipe, wherein the improvement comprises: a) at least one first heating element on an outside of the cooling pipe; b) at least one second heating element on an outside of the downcomer pipe; and c) a plurality of thermocouples that measure the temperature of the glass stream at an inflow end and an outflow end of each first heating element and each second heating element; wherein an error in flow rate is determined by a calculation of a balance of energy for the first heating element; such that an energy may be redistributed to the first heating element and the second heating element, thus changing an average glass viscosity in the downcomer pipe, such that a flow rate of glass is maintained at a substantially constant value.
 16. The improved apparatus of claim 15, wherein a total energy remains constant.
 17. The improved apparatus of claim 15, further comprising a plurality of cooling zones at a same location as the first heating element and the second heating element.
 18. The improved apparatus of claim 17, wherein the cooling zones measure an energy flux.
 19. The improved apparatus of claim 15, wherein the thermocouples are immersed in the glass stream.
 20. The improved apparatus of claim 19, wherein defects caused by a flow of glass in proximity of the thermocouples end up in at least one unusable bead at either end of a formed glass sheet.
 21. The improved apparatus of claim 15, further comprising a plurality of second heating elements.
 22. The improved apparatus of claim 21, further comprising a plurality of cooling zones at a same location as the first heating element and the second heating element.
 23. The improved apparatus of claim 22, wherein the thermocouples are immersed in the glass stream.
 24. A method of supplying a constant flow of glass to a glass forming process, using an apparatus comprising a cooling pipe for cooling the glass, a downcomer pipe for controlling the flow of molten glass, a bowl for connecting the cooling pipe to the downcomer pipe, at least one first heating element on an outside of the cooling pipe, at least one second heating element on an outside of the downcomer pipe; and a plurality of thermocouples that measure the temperature of the glass stream at an inflow end and an outflow end of each first heating element and each second heating element, comprising the steps of: a) calculating a balance of energy for the first heating element to determine an error in a flow rate; and b) redistributing an energy to the first heating element and the second heating element, thus changing an average glass viscosity in the downcomer pipe, such that the flow rate of glass is maintained at a substantially constant value.
 25. The method of claim 24, wherein a total energy remains constant.
 26. The method of claim 24, further comprising the step of maintaining an outlet temperature of the glass exiting the downcomer pipe at a fixed value.
 27. The method of claim 24, wherein the apparatus further comprises a plurality of cooling zones at a same location as the first heating element and the second heating element.
 28. The method of claim 27, further comprising the step of measuring an energy flux from the cooling zones.
 29. The method of claim 28, further comprising the step of maintaining the outlet temperature of the glass flowing from the downcomer pipe at a fixed value.
 30. The method of claim 24, wherein the thermocouples are immersed in the glass stream.
 31. The method of claim 30, wherein defects caused by a flow of glass in proximity of the thermocouples end up in at least one unusable bead at either end of a formed glass sheet.
 32. An improved apparatus for forming sheet glass, wherein the apparatus comprises an inflow pipe for delivering molten glass, a trough for receiving molten glass that has sides attached to a wedged shaped sheet forming block that has downwardly sloping sides converging at a bottom of the wedge such that a glass sheet is formed when molten glass flows over the sides of the trough, down the downwardly sloping sides of the wedged shaped sheet forming block and meets at the bottom of the wedge, wherein the improvement comprises: a) a first inflow end compression block inserted into a first cavity at an inflow end of the forming block, shaped to apply at least a portion of the inflow end compression force at an inflow end compression surface at zero cavity depth; and b) a second far end compression block inserted into a second cavity at a far end of the forming block; such that a longitudinal compressive force is applied to a bottom of the first cavity and a bottom of the second cavity to counteract a thermal creep deformation effect of a gravitational force from a weight of the forming block such that a thickness profile of a glass sheet remains substantially constant.
 33. The improved apparatus of claim 32, wherein a depth of the first cavity and a depth of the second cavity are independent and range from 0 to 40 percent of a length of the bottom of the wedge.
 34. The improved apparatus of claim 33, wherein the depth of the first cavity ranges from 20 to 35 percent of a length of the bottom of the wedge.
 35. The improved apparatus of claim 34, wherein the depth of the second cavity ranges from 10 to 25 percent of a length of the bottom of the wedge.
 36. The improved apparatus of claim 35, wherein the first inflow end compression block has a substantially higher resistance to thermal creep than the forming block and a cross-sectional area that maintains a force at a bottom of the first cavity constant when both the compression block and the forming block deform due to thermal creep.
 37. The improved apparatus of claim 36, wherein the first inflow end compression block and the first cavity have a stepped design in order to apply compression forces at multiple depths of the first cavity.
 38. The improved apparatus of claim 32, wherein the second far end compression block is shaped to apply at least a portion of the far end compression force at a far end compression surface at zero cavity depth.
 39. The improved apparatus of claim 38, wherein the second far end compression block has a substantially higher resistance to thermal creep than the forming block and a cross-sectional area that maintains a force at a bottom of the second cavity constant when both the compression block and the forming block deform due to thermal creep.
 40. The improved apparatus of claim 38, wherein the second far end compression block applies all of the far end compression force at the far end compression surface at zero cavity depth.
 41. A method for forming sheet glass of constant thickness, wherein the apparatus includes an inflow pipe for delivering molten glass, a trough for receiving molten glass that has sides attached to a wedged shaped sheet forming block that has downwardly sloping sides converging at the bottom of the wedge such that a glass sheet is formed when molten glass flows over the sides of the trough, down the downwardly sloping sides of the wedged shaped sheet forming block and meets at the bottom of the wedge, comprising the steps of; a) measuring a thickness profile of a manufactured glass sheet at a time during a manufacturing campaign; b) calculating a deformed shape of the forming block; and c) determining at least one change in at least one force applied to the forming block that changes a shape of the forming block to produce a more uniform thickness distribution using finite element analysis.
 42. The method of claim 41, wherein the apparatus further comprises: a) a first inflow end compression block inserted into a first cavity at an inflow end of the forming block; b) a second far end compression block inserted into a second cavity at a far end of the forming block; c) a third inflow end compression block at a surface of the first cavity at the inflow end of the forming block; and d) a fourth far end compression block at a surface of the second cavity at the far end of the forming block; wherein the method further comprises the step of applying a longitudinal compressive force to the first inflow end compression block, the second far end compression block, the third inflow end compression block, and the fourth far end compression block to counteract a thermal creep deformation effect of a gravitational force from a weight of the forming block.
 43. The method of claim 41, wherein step b) uses computational fluid dynamics to calculate the deformed shape.
 44. The method of claim 41, wherein step b) uses at least one test result from oil modeling to calculate the deformed shape.
 45. The method of claim 41, wherein the apparatus further comprises: a) a first inflow end compression block at an inflow end of the forming block; and b) a second far end compression block at a far end of the forming block; wherein the method further comprises the step of applying a longitudinal compressive force to the first inflow end compression block and the second far end compression block to counteract a thermal creep deformation effect of a gravitational force from a weight of the forming block.
 46. The method of claim 41, wherein the apparatus further comprises: a) a first inflow end compression block inserted into a first cavity at an inflow end of the forming block; b) a second far end compression block at a far end of the forming block; and c) a third inflow end compression block at a surface of the first cavity at the inflow end of the forming block; wherein the method further comprises the step of applying a longitudinal compressive force to the first inflow end compression block, the second far end compression block, and the third inflow end compression block to counteract a thermal creep deformation effect of a gravitational force from a weight of the forming block.
 47. An improved apparatus for forming sheet glass, wherein the apparatus includes an inflow pipe for delivering molten glass, a trough for receiving molten glass that has sides attached to a wedge shaped sheet forming block that has downwardly sloping sides converging at the bottom of the wedge such that a glass sheet is formed when molten glass flows over the sides of the trough, down the downwardly sloping sides of the wedged shaped sheet forming block and meets at the bottom of the wedge, an open bottom first temperature controlled chamber enclosing the inflow pipe, the trough, and the wedge shaped sheet forming block, wherein the improvement comprises: at least one cooling block comprising a wedge-shaped bottom and a horizontal dimension that is substantially the same as a horizontal dimension of the forming block located below the bottom of the wedge such that a glass flowing from the bottom of the wedge descends onto the top of the cooling block, then flows vertically down each side of the cooling block to the wedge shaped bottom of the cooling block where glass from each side joins to form a molten sheet which passes into a second temperature controlled chamber where the glass solidifies; wherein the cooling block is contained within a third temperature controlled chamber; and wherein a vertical dimension of the cooling block is adequate to cool vertically flowing glass from a cooling block glass inflow temperature to a glass sheet forming temperature at the wedge shaped bottom of the cooling block.
 48. The improved apparatus of claim 47, further comprising at least one compression block at each bottom end of the cooling block to provide a compression force in the bottom of the cooling block to counteract a gravitational force caused by a weight of the cooling block and glass flowing on the cooling block that will deform the cooling block due to thermal creep.
 49. The improved apparatus of claim 47, wherein the cooling block further comprises at least one edge director at each end to maintain a substantially constant width of the vertically flowing glass.
 50. The improved apparatus of claim 49, further comprising a plurality of heaters which regulate a temperature of the edge directors and a temperature the glass flowing on the edge directors to counteract devitrification effects of the vertically flowing glass.
 51. The improved apparatus of claim 49, further comprising a plurality of edge director fences skewed outward away from a center of the cooling block to create a wider glass sheet.
 52. The improved apparatus of claim 51, wherein a skew angle of the edge director fences and a shape of the edge director fillet surface are determined via an oil model using a Capillary Number for the oil which is the same as the Capillary Number for the molten glass.
 53. The improved apparatus of claim 51, wherein a skew angle of the edge director fences and a shape of the edge director fillet surface are determined by computational fluid dynamics.
 54. The improved apparatus of claim 47, further comprising a pair of sliding doors located at the bottom of the first temperature controlled chamber.
 55. The improved apparatus of claim 54, wherein a first localized pressure in the first temperature controlled chamber at the pair of sliding doors and a second localized pressure in the second temperature controlled chamber at the pair of sliding doors is equalized.
 56. The improved apparatus of claim 47, further comprising a pair of sliding doors located at a bottom of the third temperature controlled chamber.
 57. The improved apparatus of claim 56, wherein a first localized pressure in the second temperature controlled chamber at the pair of sliding doors and a second localized pressure in the third temperature controlled chamber at the pair of sliding doors is equalized.
 58. A method for forming sheet glass of constant thickness, wherein the apparatus includes an inflow pipe for delivering molten glass, a trough for receiving molten glass that has sides attached to a wedged shaped sheet forming block that has downwardly sloping sides converging at the bottom of the wedge such that a glass sheet is formed when molten glass flows over the sides of the trough, down the downwardly sloping sides of the wedged shaped sheet forming block and meets at the bottom of the wedge, comprising the steps of; a) measuring a thickness profile of a manufactured glass sheet at a time during a manufacturing campaign; and b) determining at least one change in at least one force applied to the forming block that changes a shape of the forming block to produce a more uniform thickness distribution using finite element analysis and computational fluid dynamics.
 59. The method of claim 58, wherein step b) uses at least one test result from oil modeling to calculate the deformed shape.
 60. The method of claim 58, wherein the apparatus further comprises: a) a first inflow end compression block at an inflow end of the forming block; and b) a second far end compression block at a far end of the forming block; wherein the method further comprises the step of applying a longitudinal compressive force to the first inflow end compression block and the second far end compression block to counteract a thermal creep deformation effect of a gravitational force from a weight of the forming block.
 61. The method of claim 58, wherein the apparatus further comprises: a) a first inflow end compression block inserted into a first cavity at an inflow end of the forming block; b) a second far end compression block at a far end of the forming block; and c) a third inflow end compression block at a surface of the first cavity at the inflow end of the forming block; and wherein the method further comprises the step of applying a longitudinal compressive force to the first inflow end compression block, the second far end compression block, and the third inflow end compression block to counteract a thermal creep deformation effect of a gravitational force from a weight of the forming block.
 62. The method of claim 58, wherein the apparatus further comprises: a) a first inflow end compression block inserted into a first cavity at an inflow end of the forming block; b) a second far end compression block inserted into a second cavity at a far end of the forming block; c) a third inflow end compression block at a surface of the first cavity at the inflow end of the forming block; and d) a fourth far end compression block at a surface of the second cavity at the far end of the forming block; wherein the method further comprises the step of applying a longitudinal compressive force to the first inflow end compression block, the second far end compression block, the third inflow end compression block, and the fourth far end compression block to counteract a thermal creep deformation effect of a gravitational force from a weight of the forming block.
 63. An improved apparatus for forming sheet glass, wherein the apparatus includes an inflow pipe for delivering molten glass, a trough for receiving molten glass that has sides attached to a wedge shaped sheet forming block that has downwardly sloping sides converging at the bottom of the wedge such that a glass sheet is formed when molten glass flows over the sides of the trough, down the downwardly sloping sides of the wedged shaped sheet forming block and meets at the bottom of the wedge, an open bottom first temperature controlled chamber enclosing the inflow pipe, the trough, and the wedge shaped sheet forming block, wherein the improvement comprises: at least one edge director at each end of the forming block to maintain a substantially constant width of the vertically flowing glass; and a plurality of edge director fences skewed outward away from a center of the forming block to create a wider glass sheet.
 64. The improved apparatus of claim 63, wherein a skew angle of the edge director fences and a shape of the edge director fillet surface are determined via an oil model using a Capillary Number for the oil which is the same as the Capillary Number for the molten glass.
 65. The improved apparatus of claim 63, wherein a skew angle of the edge director fences and a shape of the edge director fillet surface are determined by computational fluid dynamics.
 66. An improved platinum delivery system comprising: a) a finer for removing bubbles from molten glass; b) a cooling pipe for cooling the glass to the required process delivery temperature; c) a plurality of heating elements comprising at least a first heating element and a second heating element on an outside of the delivery system; and d) a plurality of thermocouples that measure a temperature of a glass stream at an inflow end and an outflow end of each heating element on the delivery system; wherein an error in a flow rate is determined by a calculation of a balance of energy for the two heating elements; such that an energy may be redistributed to the two heating elements, thus changing an average glass viscosity in the delivery system, such that the flow rate of glass is maintained at a substantially constant value.
 67. The apparatus of claim 66, further comprising a plurality of cooling zones at a same location on the delivery system as the heating elements.
 68. The apparatus of claim 66, wherein the cooling zones measure an energy flux.
 69. The apparatus of claim 66, wherein the thermocouples are immersed in the glass stream.
 70. The apparatus of claim 66, further comprising a stirrer located between the finer and the cooling pipe.
 71. The apparatus of claim 66, wherein the first heating element and the second heating element are located on an outside of the finer.
 72. The apparatus of claim 66, wherein the first heating element and the second heating element are located on an outside of the cooling pipe.
 73. The apparatus of claim 66, wherein the first heating element is located on an outside of the finer and the second heating element is located on an outside of the cooling pipe.
 74. A method of supplying a constant flow of glass for a platinum delivery system, using an apparatus comprising a finer for removing bubbles from molten glass, a cooling pipe for cooling the glass to the required process delivery temperature, a plurality of heating elements comprising at least two heating elements on an outside of the delivery system, and a plurality of thermocouples that measure a temperature of a glass stream at an inflow end and an outflow end of each heating element on the delivery system, comprising the steps of: a) calculating a balance of energy for the two heating elements to determine an error in a flow rate; and b) redistributing an energy to the two heating elements, thus changing an average glass viscosity in the delivery system, such that the flow rate of glass is maintained at a substantially constant value.
 75. The method of claim 74, further comprising the step of maintaining an outlet temperature of the glass flowing from the delivery system at a fixed value.
 76. The method of claim 74, wherein the apparatus further comprises a plurality of cooling zones at a same location on the delivery system as the heating elements.
 77. The method of claim 76, further comprising the step of measuring an energy flux from the cooling zones.
 78. The method of claim 76, further comprising the step of maintaining the outlet temperature of the glass flowing from the delivery system at a fixed value.
 79. The method of claim 74, wherein the apparatus further comprises a stirrer located between the finer and the cooling pipe. 